Sonic pile driver



July 20, 1965 w. B. GOODMAN SONIC FILE DRIVER Filed Jan. 17, 1962 F/gJa.

4 74 35c g 32 3s Q 5 "YD 14 Sheets-Sheet l IN V EN TOR. WILLARD B. GOODMAN July 20, 1965 W. B. GOODMAN SONIC PILE DRIVER Filed Jan. 17, 1962 14 Sheets-Sheet 2 IN VEN TOR. WILLARD B. GOODMAN y 1965 w. B. GOODMAN 3,195,659

some PILE DRIVER Filed Jan. 17, 1962 14 Sheets-Sheet 5 i i fII/IAW/IIIA 550 1 453 :i 23 31s w 317 WILLARD B. GOODMAN 7' TOHNEYS July 20, 1965 w. B. GOODMAN 3,195,659

some PILE DRIVER l4 Sheets-Sheet 4 Filed Jan. 17, 1962 24 INVENTOR.

WILLARD B. GOODMAN A mq/vz s y 0, 1965 W. B. GOODMAN 3,195,659

some FILE DRIVER Filed Jan. 17, 1962 1 sh t s 5 INVIENTOR. WILLARD B. GOODMAN f i flrjamvsrs July 20, 1965 w. B. GOODMAN SONIC PILE DRIVER l4 Sheets-Sheet 6 Filed Jan. 1'7, 1962 INVENTOR. WILLARD B. GOODMAN i; Ar a/msrs y 1955 w. B. GOODMAN 3,195,659

some FILE DRIVER Filed Jan. 17, v1962 ,14rSheets-Sheei 8 l5 INVENTOR. 156m 6 WILLARD B. GOODMAN A'rrmmsys July 20, 1965 w. B. GOODMAN soriIc PILE DRIVER 14 Sheets-Sheet 9 Filed Jan. 17, 1962 INVENTOR. WILLARD B. GOODMAN Arr RIVEYS July 20, 1965 W. B. GOODMAN SONIC PILE DRIVER Filed Jan. 1'7, 1962 14 Sheets-Sheet 10 m w n .1 2 M 2 0 INVENTOR. WILLARD B. GOODMAN A ronmsrs July 20, 1965 w. B. GOODMAN SONIC FILE DRIVER 14 Sheets-Sheet 11 Filed Jan. 1'7, 1962 F lg. ZZZ

VEN TOR.

GOODMAN WILLARD B.

July 20, 1965 w, BBBBBBB AN 3,195,659

July 20, 1965 w. B. GOODMAN SONIC FILE DRIVER 14 Sheets-Sheet 15 Filed Jan. 17, 1962 saw INVEN TOR. WILLARD B. GOODMAN July 20, 1965 w. B. GOODMAN INV TOR. WILLARD B DMAN 1 Arman/Er:

United States Patent 3395,65? GNIC FILE DRIVER Willard It. Goodman, lherman Galas, Calif assignor to Albert G. Bodine, In, doing business as Bodine Soundrive Company, Los Angeles, Calil Filed Ian. 17, 1962, Ser. No. 166,745 13 Claims. (Cl. 1755) 'This invention relates generally to sonic pile drivers, of the class disclosed in prior United States Patent No. 2,975,846, and which may be characterized generally as comprising means for setting up sonic waves in the pile while exerting a downward biasing force on the pile.

The acoustic theory underlying sonic pile drivers is set forth in said Patent No. 2,975,846, and need not be repeated herein in full detail. Briefly, a generator of sonic vibrations, i.e., a vibration generating oscillator, is acoustically coupled to the pile, with proper attention to adjustment of the output impedance of the oscillator to that of the pile with the pile in tight engagement with the earth, so as to set up longitudinal sonic wave action in the pile. The oscillator is operated, broadly speaking, so as to set up a resonant longitudinal standing wave in the pile. Assuming operation in the fundamental frequency range, the frequency for resonance may range, during operation, between C/2L and C/4L, where L is the equivalent length of the pile and acoustically coupled-in mass of the pile driver, and C is the velocity of sound in the medium of the pile. For the longer length piles, operation may be at a harmonic of the fundamental frequency.

Sonic pile driving equipment of this class, embodying a number of features of the present invention, has demonstrated, in field tests, the ability to out-drive conventional steam hammer pile drivers by an average ratio of the order of 20 to 1, and in some instances has substantially exceeded that ratio.

Tests carried on to date with equipment of this type have demonstrated the need for powerful sonic drive, flexibility in the drive, accommodation to turning and/ or tilting movements of the pile, and good compliant support for the motor means on the pile, whereby the motor means rests on the pile, but is virtually isolated from the sonic wave action or vibration set up in certain parts of the equipment and in the pile.

Objects of the invention include the provision of a sonic pile driver which is improved as regards power, flexibility and accommodation to movement of the pile during sonic wave driving, such as twisting or tilting.

A further object is to provide an improved sonic pile driver incorporating a compliant support for the motor means, whereby the motor means exerts weight on the pile, but is eompliantly isolated from the sonic frequency vibration of the pile.

A further object is the provision of a flexible driver of novel nature between the motor means and the vibration generator or oscillator driven thereby, such that the oscillator is permitted a large amplitude of vibration, but only a small proportion of this vibration reaches back to the motor means,

A further object is the provision of a sonic pile driver having a novel means for picking up a pile from a horizontal position and hoisting it to a vertical driving position.

A further object is the provision of a novel and effective means for increasing the downward biasing force on the pile during driving.

Other objects will appear in the course of the ensuing description of a present illustrative embodiment of the invention, reference being bad to the accompanying drawings, in which:

FIG. 1 is a somewhat diagrammatic perspective view of 3,l%,b Patented July 20, 1.965

'ice

a sonic pile driving system in accordance with the invention;

FIG. 1a is an enlarged fragmentary view, in side elevation, of the upper end portion of the system of FIG. 1;

FIG. 2 is a front elevational view of the sonic pile driving machine of the invention, shown together with a portion of the leads on which the machine is vertically guided;

FIG. 3 is a plan view of the machine of FIG. 2, the oscillator and pile clamping means being shown in phantom lines in a tilted position to facilitate acceptance of the pile from an initial horizontal position at ground level;

FIG. 4 is a side elevational view of the machine of FIG. 3, as seen from the right in FIG. 3, showing the pile driving machine near the lower end of the leads, and showing, in phantom lines, the oscillator, pile clamp and other portions of the machine tilted into a horizontal position to facilitate acceptance of the pile from an initial horizontal position at ground level.

FIG. 5 is a section taken on line 5-5 of FIG. 3;

FIG. 5a is a detail section taken on line 5a-5a of FIG. 5;

FIG. 6 is a section taken on line 6-6 of FIG. 6;

FIG. 7 is an enlargement of a portion of FIG. 6, with parts broken away to show underlying portions in section;

FIG. 8 is a section taken on line 8-8 of FIG. 6, but with the oscillator and other interior parts in elevation;

FIG. 9 is a vertical plan view of the parts inside the exterior casing of FIG. 8;

FIG. 10 is a section taken on broken line ill-10 of FIG. 6;

FIG. 11 is an elevational view of the lower end portion of a tiltable housing of the apparatus, with parts broken away;

FIG. 12 is a section taken as indicated by line 12-42 of FIG. 11;

FIG. 13 is a section taken on broken line I3I3 of FIGS. 12 and 14;

FIG. 14 is a section taken in accordance with broken line 14-14 of FIG. 13;

FIG. 15 is a section taken on line 15I5 of FIG. 14;

FIG. 16 is a detail section taken on line re rs of FIG. 12;

FIG. 17 is a detail section taken on line 17-17 of FIG. 14;

FIG. 18 is a section taken on line 1818 of FIG. 8; also on line 18-18 of FIG. 19;

FIG. 19 is a section taken on line 19-19 of FIG. 18;

FIG. 20 is a sectional view taken in accordance with line 2ll-2tl of FIG. 19, but with the crankshaft, servoroller and inertia ring angularly displaced 90 from the position of FIG. 19, i.e., with the crankshaft turning through its lowermost position;

FIG. 21 is a section taken on line 2121 of FIG. 26;

FIG. 22 is a section on line 22-22 of FIG. 20;

FIG. 23 is a section on line 2323 of FIG. 20;

FIGS. 24 and 25 are diagrammatic views illustrating the performance of the vibration generator of FIGS. 20-23;

FIG. 26 is a longitudinal medial sectional view of the pile clamp, being a section on line 26-26 of FIG. 27; and

FIG. 27 is a transverse section on line 27-27 of FIG. 26.

The invention makes use of certain pile driver transport and handling equipment now conventional in hammer type pile drivers. Thus, as shown in FIG. 1, a vehicle 36 equipped with crawlers 31 pivotally supports, at 32, a boom 33, the upper end of which in turn pivotally supports, at 3 the usual leads 35 comprising a box-frame beam structure including a pair of tubular vertical front described in more particular hereinafter.

legs 36 on and between which a frame work for the sonic driving machine 37 is vertically guided, much as in the conventional hammer. The sonic driving machine 37 delivers to the pile P a cyclic forcewave characterized by a succession of high amplitude force impulses at a resonant standing wave frequency. of the pile,- as will be A so-called spotter, comprisinga telescopic beam structure 38, adjustable -in,length, is connected between the vehicle 30 and the lower end of the leads 35, and conventional cable gear 39 is used to raise and lower the boom, all as is fully-understood in the pile driving art, and will require no further description herein. -The so-called leads '35 comprise, in addition to the aforementioned vertical front legs 36, a pair of rear legs 36a, and suitable horizontal bracing 86b and diagonal bracing 360 as indicated. The sonic machine is suspended from the upper end of the leads by a block and tackle system as will be described. While the present pile driver is capable of or adaptable to the driving of various types of pile, such as tubular, open or-closed, bottom, tubular corrugated, inside or outside mandrel driven, H-section, etc., the invention is here illustrated as driving a tubular pile P (see FIG. 2). The upper end of this pile is rigidly clamped by a hydraulically actuated clamp or coupling means generally designated by the numeral 4th anddescribed in detail hereinafter. As shown best'in FIG. 6, a column generally designated by numeral 41, and made up of later described componezits, extends upwardly from clamp means 40 and car ries at its top the vibration generator or oscillator42. In operation, the body of this oscillator delivers to the upper'end of column 41 a cyclic vertically oriented al-' terna'ting force of large magnitude or impulse, and this cyclic force is transmitted through column41 and clamp means 40 to the upper end of the pile. The frequency of this cyclic force is made to bein the range of a resonant standing wave frequency of the pile, in general as disclosed in the aforesaid Patent No. 2,975,846.

The sonic pile driving machine of the invention, in its present illustrative form, has two separate motor means for driving the oscillator 42, comprising, preferably, and

in this instance, two internal combustion: engines 44 (FIGS. 2,3 and 4), d'isp-osed on opposite sides of the leads, in end to end opposition, with their drive shafts 45 in axial alignment. T hecommon axis of the drive shafts intersects the vertical axis of the pile P and the column 41.

Extending horizontally over and longitudinally of the two engines is a horizontal support beam structure 46 (FIGS. Z and 3) comprised of a center beam 47, two

short frame beams 48 bolted to and extending outwardly from the ends of center beam 47, and two tubular engine support beams 49 extending outward from frame beams 48 and overlying the two engines. The two tubular beams 49 have braced flanges 50 suitably secured to mat: ing flanges 51 on the frame beams 48.. Tubular beams 49 are closed at the ends and serve as air receivers, for a purpose to be mentioned hereinafter. -A standard com pressor, not shown, maintains these receivers filled with air under necessary compression. Extending laterally and downwardly from the tubular beams 48 are engine support'framing means including lateral members 53 and vertical channel members 54 carrying engine support brackets 55 (FIGS. 3, 4 and 5). Connected to the lower ends of members 54 are lower horizontal frame members 56. Platforms 58 extend rearwardly from the rearward frame members 56 (FIGS. 3 and 4) and on at least one of these platforms is erected a hand rail59 and a seat 60 for an operator. An instrument panel, in convenient reach of the operators position, is indicated at 61.

Fuel tanks for the engines are indicated at 62, supported below the engines by frame members 56, and the engines are shown with exhaust pipes 63, muffiers 64, and air cleaners 65 (FIG. 2).

The entire sonic machine may be hoisted or lowered by means of block and tackle gear 66 including double sheaves 67 in the top of the leads, a cable 68, and a block 69 having an eye 70 for connection of one end of the cable 68, and a sheave 71, mounted at the center of beam 46 (FIGS. 1-5). The cable 68 goes from eye 76 over one sheave 67 at the top of the leads, then down and around sheave 71, then up and over the second sheave 67, then down the back of the leads over guide sheaves 72a and 72b, under a sheave 73 mounted on the leads adjacent the upper end of boom 33, under another sheave 74 nearthe lower end of the boom, and thence to a power winch (not shown) within the vehicle 30. During hoisting or'lowering movement of the sonic machine by this cable system, the machine is guided by the tubular mem bers of the leads 36, as later described.

The frame beams 48 have depending double-walled legs 75 (FIGS. 5, 6 and 7) formed, in axial alignment with the engine drive shafts, with inwardly projecting hubs '76. These hubs 76 receive bearing sleeves 77 containing roller bearings '78 for drive sleeves 79 formed with internal splines 86. 1 As shown best in FIG. 7, each of the aforementioned engine shafts 45 is coupled through coupling 83 to a cup 84- containing internal splines 85, and a drive shaft 86 has on one end ahead 87 received inside cup 84 and formed with arcuatesplines 88 meshing with spline 85,- and has on the other end a head 90 received inside the corresponding end portion of sleeve '79 and formed with arcuate splines 91 meshing with splines 86. The arcuate splines on heads 87 and 9% permit the shaft 86 to move angularly through a limited extent while driving the sleeve 79 from the engine shaft 46. Received in the opposite end portion of sleeve 79 is a head 94, provided with arcuate splines 95 meshing with splines 80, and formed on the end of a shaft- 96. The other end of this shaft 96 drives certain gears leading tothe oscillator, as will later. be explained. An intermediate partition 97 in sleeve 79, engageable by heads 91' and 95, limits endwise movement of the shafts 86 and 96 inwardly into sleeve 79. a The two frame hubs 76 (FIG, 6) form axially aligned trunnions on which the oscillator and certain associated gearlng and other components of the mechanism are pivotally mounted. Bearing bushings 100' (FIGS. 6 and 7) surround trunnions 76, and rotatable on bushings 160 are frame members or collars 101 which are disposed about the trunnions, and to which are welded a top frame ring 102. An inner cylindrical wall 163 is welded to the inner edge of ring 162 and to members 101, and an outer cylindrical wall 104 is welded to the outer edge of ring 102, just outside members 101, and being apertured, as at 105 (FIG. 7), to receive outwardly projecting annular portions 106 of the members 101.

,A heavy'frusto-conical plate 108 is welded to walls 103 and 104, just below collars 101, and carries, at its lower, inner edge, a mounting ring 169 engaged by a pcripheral flange 110 on the rim of a heavy support plate 111, to be described in more detail hereinafter, but which may be stated at this point to be supported compliantly, in the vertical direction, by the upper end of an air spring generally designated at 111. It may also be stated at this point that the weight of the two engines is imposed throughthe beam 46, frame legs 75, trunnions 76, frame collars 191. cylindrical walls 103 and 104. frustoconical plateltltl, and plate 111, onto the upper end of the air spring. In fact, as will appear from what follows, the weight of the entire machine, excepting for the oscillator 42, its supporting column 41, the later described air spring pistons, and the hydraulic pile clamp 40,-is transferred throughthe plate 111 to the upper end of the air spring. The air under compression in this air spring 112 transfersthis entire load complia'ntly to the aforementioned column 41 mounted on'the pile, and thus to the framework adapted forvertical guidance by the leads;

while trunnioned to the arms 75 of this framework is a frame means 161, 1.92, 1 33, 1&4, 168 and 111 imposing the load of this structure on the top of the air spring.

The air spring 111, in a present illustrative form, is made up as follows (FEGS. 6, 13, 14 and 15): The hydraulic clamp 45) for the pile includes an upper inverted cup 115 (FIGS. 6 and 26) having a marginal flange 116 secured, as by screws 117, to the bottom of a lower inverted clamp cup 118, into which the upper end of the pile is received and clamped, as later described. The upper cup 115 has a cylindrical side wall 11?, and a flat top 12%) provided with a central boss 121. Mounted on the top 12% of cup 115 is the lowermost of a plurality of circular plates ins, here three in number, serving as pistons of the air spring. The two plates 124 above the lowermost one are separated from the latter and from each other by thick spacer washers 125, and a cylindrical head 12-6, of the same diameter as the washers, seats on the uppermost plate The plates 124 have central tioning apertures 124a receiving the boss 121 on cup 1;), receiving similar bosses 127 formed on the washers 125 and head 1%. The cup 115, spacer washers and head 12s are connected by tie rods 1%, the upper ends of which are threaded into a flange 131 on the lower end of a tubular stern 132 forming an upper portion of he column 41, and the lower ends of which are threaded to receive nuts 133, as shown. An enlarged cylindrical head at the upper end of stem 132 is secured, as by studs 135, to the cylindrical base part 136 or" the oscillator body 137. The cup 115, plates 12%, washers 125, head 125, and stem 132, comprise the aforementioned column 4-1 by which the oscillator body is supported on the upper end of the pile.

The piston plates 124 are positioned in chambers 14% whose side walls are defined by cylindrical rings 141. En-

gaging and sealed to the uppermost ring 141 is an air spring cover plate 143, bearing the down load of the plate 111, and formed with a central bore 144 (FIG. 13) whicr receives, with a small clearance, the head member 1126 of column d1. Vertically spaced piston rings 1415 are used around the head member 125 to afiord a pressure tight seal, as shown.

At the bottom of the air spring assembly is a bottom cover plate 147 (FIG. 13), engaging the lower end of the lowermost ring 3421, and bored, as at 1 67a, to receive. with clearance, the cylindrical side wall 117 of cup 115. plate 14-? is counterbored to receive a bronze bearing bi sing 1 1% for the clamp cup wall 119, and piston rings 1 seal the cover plate 1 .17 to said wall 119.

Eetween the rings id-1 are spacer rings 15% formed wi h partition walls 151 which carry bushings 152 (FIG. 135 tilting the spacer washers 125 with small annular clearance, pressure tight seals being provided therebetween by means of piston rings 153. The assembly of rings 1&1 and 15-3 and upper and lower cover plates 143 and 14-7, is secured by long bolts 141a, making up air spring housing 154. The peripheries of the piston plates 124 carry piston rings 155 which atlord pressure seals with the cylindrical inside surfaces of the ring 141.

Air under pressure is supplied to air spring chambers 1 5- 25 as shown best in FlG. 13. The pressurized air is conveyed via a hose 156 to a fitting 156a on the rim of cover plate Hose 1'56 leads from a fitting 156k on the inside of a later described housing wall, which is fed through connector 1560 (FIGS. 11 and 12) on the outside or" said wall from a hose, not illustrated, but which will be understood to lead from any suitable source of air under pressure, for example, one of the pressure reservoirs 49. The air entering fitting 156a passes through a pair of metering orifices 157 to passages 158 extending vertically through rings 141 and 159. Upper and lower ports and 16b in rings 141 provide communication between passages 1&8 and the chamber spaces above and below the pistons 124,. so that air under pressure is delivered to both of said chamber spaces. The piston rings 155 in the edges of pistons 12% control orifices 162 (FIG. 15) in the rings 141 leading to vertical air discharge passages 1&5. As seen in FIG. 14, there are a number of the vertical discharge passages 153, and a corresponding plurality of the orifices 1&2. in the mid-positions of the pistons, the orifices 162 are closed by the piston rings 155. Whenever the downward loading imposed on the air spring housing 154 exceeds a predetermined value, the air spring housing lowers relative to the pistons 124, so that orifices 162, communicate wholly or partially with the chamber spaces below the pistons. A quantity of pressure air is thus discharged from below the pistons, so that there is a pressure differential across each piston in the downward direction. It will be seen that this pressure dillerential is such that an upward force is exerted on the air spring housing, so that the latter then tends to rise. The system seeks and tends toward a condition characied by bodies of air under compression above and below the several pistons, and with suilicien-t continuous or periodic discharge of air from below the pistons to afford regulated air pressures and a regulated pressure differential which furnishes air spring support for the air spring housing and parts resting thereon. During pile driving, the pistons oscillate vertically, while the air cushions between the plates and the air spring housing lly isolate the latter from such oscillation. At the sa time, the parts resting on the air spring housing are vertically supported by the air under compression in the air spring, and whatever minor vertical vibration, if any, that may occur in the air spring housing is accommodated by the compressed air in the air spring.

it will be seen that the air spring cover has on its underside an annular abutment 165 for the uppermost piston plate 124, normally spaced thereabove, but furnishing a stop shoulder engageable against the uppermost plate 124 in event of loss of pressure in the chambers 14% above the plate 124. Similarly, the lower air spring cover 147 has an annular abutment 166, which is engagable against the lowermost plate 12d in event of an upward pull being taken on the air spring housing (under conditions to be described later) in event of loss of pressure in the chambers 14 0 below the plates 124. In normal operation, the piston plates 124 have a vibratory travel range which terminates short of the abutment shoulders 165 and 166.

Referring again to the supporting plate 111, and to FIG. 6, the periphery of said plate, as explained above, has a peripheral flange or mounting rim portion 110. Inside said rim portion, the plate has a channel portion 176 (the reason for the shape of which will appear hereinafter) inside of which is a centrally apertured dished or arcuate portion 1'71, defined by arcs struck about a center point T (FIG. 6) which is at the intersection of the axes of the engine shafts with the vertical axis of the column 41 and the pile. This arcuate portion 1171 surrounds the hub portion 173 on the top of cover plate 143, there being a substantial annular clearance between these parts, as shown. A bearing ring 174 seated in a pocket in the top of plate 14-3 has a concave arcuate upper face mating the convex arcuate lower face of plate portion 171. A bearing ring 176 has a convex arcuate lower face mating the concave upper face of plate portion 171. This bearing ring 176 fits onto the tubular lower end portion 178 of a sleeve 13%, said tubular portion 173 engaging an annular seat on air spring cover 143 and being secured thereto, as shown best in FIG. 6. The arcuate portion 171 of plate 111 has a free sliding fit between the bearing rings 1'74 and 176.

Sleeve 180 has, just above tubular portion 178, an annular flange 181, the under side of which engages bearing ring 176, and which in turn supports certain parts of the mechanism, as will presently appear. The sleeve 180 rises to a level just above the lower end of the cylindrical base part 136 of the oscillator body or housing, having at its uppermost end an internal shoulder 183 which fits oscillator base part 136 and cylindrical head 134 of stem 132 with clearance, and under which is confined a bronze bear-' ing bushing 184 for said cylindrical head 134.

Referring again to FIGS. 6 and 7, the aforementioned shafts 96, understood to be driven in opposite directions on their common axis from the two engines, have on their ends nearest the pile axis heads 1% formed with arcuate splines 191 which mesh with internal splines inside the bores of bevel gears 192. Each of these gears 192 has a sleeve portion 193 turning in a bearing 194, the outer cylindrical case 195 of which has an intermediate mounting flange 196. The two bearing cases 195 are received in cylindrical openings 197 formed in opposite sides of a frame ring 198 supported on and secured to a peripheral portion of the. aforementioned flange 181, as clearly shown in FIGS. 6 and 7. The bearing mounting flanges 196 engage the frame ring 198 around the openings 197, and are secured thereto as shown.

Oppositely rotating bevel gears 192 mesh with a ring gear 200 which surrounds sleeve 181 with annular clearance, and which is secured to an annular flange 210 on the lower end of a telescopic drive sleeve assembly 211 (FIG. 7) surrounding and relatively rotatable about the aforementioned sleeve 180. Preferably, the sleeve assembly 211 includes a lower sleeve portion 212 reaching upwardly from flange 210, and carrying a bronze bushing 213 rotatable on sleeve 180, an opposed upper sleeve portion 214 spaced above sleeve portion 212, and carrying a bronze bushing 215 also rotatable on sleeve 139, and an intermediate interconnecting sleeve 216 having portions overlapping said upper and lower sleeve portions 212 and 214, and drivingly connected therewith by splines 218.

l The flange 210 at the bottom of the drive sleeve assembly 211 has secured to its bottom a bronze bearing ring 220, which bears against and turns on the flange 181. The upper side of this flange 210 engage a bronze bearing ring 220' supported by frame ring 198 (FIG. 6). The upper end of the upper sleeveportion 214 of sleeve assembly 211 has internally formed therewith a ring gear 221, meshing with and driving, in opposite directions on their common axis, two bevel gears 222 of a. turret 224 through which the oscillator 42 is driven. The telescopic feature of sleeve assembly 211 is for the accommodation of longitudinal expansion or contraction owing to temperature changes, and is such as to assure that the working parts at both the upper and lower ends of this sleeve assemblymaintain proper positions with reference to hearing surfaces, gears, etc.

The aforementioned bevel gears 222 are on gear sleeves 230 (FIG. 6 journalled in suitable bearings in bearing housings 231 which are secured in opposite sides of a turret frame ring 232, and the latter has at the-bottom a tubular extension 233 an a downwardly presented bear: ing face 234 outside thereof which engages a bronze hearing ring 235 seated in the previously described frame ring 198. Turret frame ring 232 is thus rotatable on frame ring 198. Turret frame ring 232 also has, at the top, an internal cylindrical bearing surface 238 and an upwardly facing bearing surface 239 which engage a bronze bearing ring 240 secured to a flange 241 on the upper end of a cap member 242 secured over and to the upper end of sleeve 180.

Secured to turret frame ring 232, at diametrically opposite locations thereon, are gear housing assemblies 250, accommodating certain gears and bearings therefor as will now be described. Each of the bevel gears 222 is internally splined, as at 251, to a shaft 252 which drives a spur gear 253 suitably journalled in the associated housing assembly 250. The gear 253 drives a spur gear 254, which in turn drives a gear 255, and the latter is on a shaft 256 carrying a larger gear 257 which meshes with and drives. a gear 258 (see FIG. '18). Gear 258 is on a gear sleeve 260 carrying a flywheel 261, and has internal splines 262 meshing with arcuate splines 263 on a spheric head 264 at one end of a drive shaft 265, the other end of which has a head 266 carrying arcuate splines 267 which mesh with splines 268 inside a coupling 269 to one side of oscillator 42. As will appear from FIGS. 6 and 9, the two gear housing assemblies 25h are so arranged that the two drive shafts 265 are parallel to one another, are on opposite sides of the oscillator 42, and are aligned with opposite halves of the latter. Also, the gear trains are so arranged that the two shafts 265 rotate in opposite directions, as will be evident.

I The oscillator contains means driven by the two shafts 265 by which the massive oscillator body 137 is set into relatively low amplitude but high force vertical vibration, and this means may, as in many known applications in the prior art, comprise two unbalanced or orbital rotors, one rotated by each of the two oppositely rotating shafts, with the rotors journalled in the body 137, and with their unbalanced masses so synchronized as to move vertically in unison, and laterally toward and from one another in unison. In such a device, the two unbalanced rotors, with their centers of gravity describing orbital paths, generate reaction forces on the body 137 which are additive in the vertical direction, but which cancel one another in the lateral direction. Powerful vertically oriented vibration forces are thereby exerted on the device on which the generator body 137 is mounted.

However, I have here shown a preferred, improved oscillator having a number of functional advantages, which are unique and of'special efficacy in a powerful sonic machine of the present character, and which has exhibited outstanding performance.

The oscillator body 137 is horizontally elongated, forming a sort of massive T-head 270 on the top of its cylindrical base part 136. This T-head has flat side faces 271 and 272, and contains parallel transverse bores 273 extending between these faces, one in each half of the T- head, and the two bores being aligned with the two aforementioned oscillator drive shafts 265. These bores 273 are lined with tightly fitted hardened steel bushings 274.

Clamped to the projecting end portions of the bushings 274 are end plates 276, the inside surfaces of which define, with bushings 274, two cylindrical chambers 278 for two relatively massive hollow cylindrical rollers or rings 280 having axial bores 231. With reference to FIGS. 18 and 19, the rings 280 are caused to roll around the inside surfaces of the bushings 273 in opposite directions by means of servo-rollers 282 which are inside of the bores of the rings 230, and which are driven in opposite direction in orbital paths by crank mechanisms 283 from oppositely rotating oscillator drive shafts 265, as shownand diagramrned in FIGS. 2025 in addition to FIGS. 18 and 19. Note that FIGS. 20-25 show the rings 2% and arms of the crank mechanisms in different positions from those of FIGS. 18 and 19, i.e., atthe bottoms of their paths of travel. The rings 282, in rolling around the bushings in the oscillator body 137, exert centrifugal forces against the latter, and the servo-rollers and their driving crank mechanisms are initially so synchronized that the rolling rings move vertically in unison, and toward and from one another in unison, so that vertical forces exerted thereby on the oscillator body 137 are additive, while lateral forces are equal and opposed, and therefore cancel.

A crankshaft 284 extending through the bore 281 in ring 280 has at its driven end an enlarged head 285 journalled in suitable bearings 286 supported by the associated end plate 276 and flange-connected to the aforementioned coupling 269 as best shown in FIG. 18. At the other end, the crankshaft has assembled therewith a disk or washer 288 supported within bearing 289 carried by the corresponding end plate 276. The latter are ported, as at 276a, to permit escape of later mentioned lubricant mist.

The crankshaft 284 has a pairof cheek plates 290 which mount a cross pin 291, and on this pin, between the two cheek plates, is an eccentric bushing 292 having short tubular end portions 293 concentric with pin 291, "but plates are provided between the ends of the rokr Y 't cheek plates, and are ion, e receiving the crankshaft (FIG. 21) to prevent them from rotatin relative to the cheek plates. 1 The operation of the servo-roller may be understood est from FIG. 23, and from FIGS. 24 and 25 which are analytic diagrams of the nice anisrn. Consider first the ring in the bushing 2'7 in oscillator body 27 3, and assume it to be in its iOJ/BmllOfii position, as in FIG. 23. The problen is to roll it around th ide of bushing of co tact ring coca progress g clockwise around the bushing. It will be seen that the ing, in this rnction, rnust actually roll in a counterclockwise direction on its own center, as indiby i same time, the ri moves l a clockwise direction, as indicated by the arrow 32. it will further be seen that the ring re '1 WlnrOlll substantial slippage on the surface of the bus ing, makes a number of orbital trips per socc "-rot'nd the bushing rack whi s substantially reater the number of bodily revolt per second, through i i the ring turns on its own center axis.

Now, to audi nce the ring beyond the lowermost ed 23, 24, 25), the servoninst be advanced slightly beyond the lower roller mo position illustrated in FXGS. 23 and 24, as to the ton indicated in the diagram of FIG. 25. In other words, the servo-roller must climb a short distance up the track afiorded by the inside bore 2-31 of the ring The servo-roller 232 is of course carried by a crank s provision for a variable dista..ce between an; axis and the axis of rotation S of the servoroller In effect, the cheek plates afford a crank arm Xtencling from the crank axis C to the axis A of the pivot pin and t e eccentric bushing 292 afifords, in effect, a drag lrnl: pivoted to such crank arm at pivot pin axis A and er ending from a A to the axis of rotation S of the servo-r c l), 2 and 25 illustrate the situati n 24- sh a beginning position, or a position 0 zero power development, and FIG. 25 showing the device n rnial operation, at which power is devmwed. The crank arm oi the eccentric bu device of 23, having a length equal to dis .ce flOfil the crankshaft axis C to axis A of the pin 2,7 The drag link AS is in efi'ect pivoed at A to cra arm CA and rotatably carryin 1 e scrvo-roler at its trailing end on axis S, with the th of the dra .4 AS equal to the distance from A of pin 231 o the S of the servo-roller. It will be seen t at the effective drag link AS trails the effective crank arm CA; and that, as the crank is rotated, centrifugal force acting on the servo-roller 252 tends to d roller outward, so as to bear against the inside ol ring 2 Also, as the roll climbs slightly up the in lined track 281 inside the ring 2 the distance from C to the point of tangency. or Contact, between roller d the inside surface 231 of ring is thereby shortened slightly. The angle between the line from C to A and the line from A to S then becomes smaller, this occurring by relative counterclockwise rotation of the eccentric bushing on the pin 1 (on axis A). The drag-link AS for the roller thus decreases its angle relative to the effective crank arm CA. Thus th servo-roller advances up the incline or" the ring track 23 the centrifugal force of the roller against the ring 289, now applied forwardl of the original oint of application (the extreme bottom) forces the ring 289 to roll forwardly on the track 274 by a corresponding distance.

The parts thus advance from the position diagrammcd in FIG. 24 to that diagrammed in FIG. 25. Referring to FIG. 24, the line of the centrifugal force F, exerted by the servo-roller 282 passes through the point of tangency or contact M between the ring 239 and the track 2 74. There is at this instant, and in this position, no force exerted by roller tending to roll the ring ass forward. in the instantly following position of FIG. 25, however, the servo-roller 282 has, as mentioned above, rolled a short distance forward, up the incline of the bore of the ring The ring has not yet advanced in the position illustrated in FIG. 25, and the parts have evidently been permitted to assmne the position illustrated by reason of the pivot at A. Now, in this position of FIG. 25, the centrifugal force F exerted by the servo-roller 232. on the inside of ring acts at an angle 6 to the line Xvi M becomes the instantaneous center about which the ring can rock or roll forward; and the distance A, the normal to the line of force F drawn from the point M, is the lever arm length at which the force P acts on the ring to rock or roll it forwardly about the instantaneous center point M. Clearly, the greater the angle 6 (which is the phase angle by which the servo-roller 282 is advanced beyond the ring 2-5) the greater the lever arm at which the force P acts on the ring 289, and the greater the power than can be developed. The pivot axis at A in the crank mechanism carryins the servo-roller readily per mits this phase angle 6 to become large, and relatively large power to be developed. Some small phase angle 6 could of course be developed without a pivot joint at A, owing to clearances and play in the parts, and for some low performance applications of an oscillator, the pivot point at A and the drag link (the eccentric bushing 2% in the case of the illustrative embodiment), can be ornited. However, for high power development, as required in a sonic pile driver, the pivot joint and drag link arrangements are of great value.

The vibration generator as described has other novel features and advantages. Outstanding among these is the relatively low torque requirement in the crankshaft for development of relatively high power. It was mentioned above that the ring rotates bodily, on its own axis, by rolling without substantial slippage on the inside of bushing 21 4. it was also mentioned that the number of such bodily revolutions per second is substantially less than the number of orbital trips which the ring 2355 makes per second around the bushing 27 i, the frequency of the latter being equal to crankshaft frequency. It will thus be evident that there is a large step down in frequency from the number of revolutions per second of the crankshaft to the number of bodily revolutions per second of the driven ring The crankshaft, thus turning at substantially higher revlutions per second than the ring 28% does so at relatively low torque for the amount of power being transmitted. The crankshaft can therefore be of lighter structure and smaller bulk than would otherwise be required. The low torque at the crankshaft for the amount of power developed is one of the principal advantages of the oscillator.

Another advantage of t e described oscillation generator over certain former generators, for example, over types having mechanically driven unbalanced rotors, resides in a decoupling of the unbalanced mass elements (the rings 289) from their driving mechanism. Thus, with the unbalanced rotor generator, there is an undesirable back reaction from the rotors to the driving mechanism as the oppositely turning rotors tend to decelerate during delivery of energy to the pile twice each cycle, and tend to accelerate during the intervening times while they are receiving energy from the power plant. Obviously there can be no such back reaction in the present generator, the rings 2% being mechanically decoupled from the driving crankshafts.

. 1 1 In the operation of the machine, the bevel gears 192 drive the-ring gear 288, and the back reaction on the gears 122 is such as tends toward producing an unwanted rota tion of the ringframe 198. To resist the torque so exerted on ring frame 1%, the latter is furnished on diametrically opposite sides, midway between the bearings 194, with pins 380 pivotally mount-ing blocks 361 (FIGS. 8 and which are received in vertical slots 382 in a pair of diametrically opposite frame brackets 303 extending upwardly from the rim of the supporting plate 111. The axis of the two pins 388* intersects the pivot center point T. The slots in the brackets 3113 hold the blocks 381 to resist the torque on the ring frame 198.

In driving a pile into the ground, the pile tends commonly not to go straight down, but to tilt to some extent, owing to nonuniform composition of the soil, or to striking of boulders. It may also tend to rotate to some extent The sonic pile driving machine of the invention accommodates for these deviations, and even takes advantage of and promotes the tendency for pile rotation.

In event of tilt of the pile from vertical, the column 41 clamped to the upper end of the pile, and supporting the oscillataor, tilts correspondingly. The surrounding assembly of sleeve 188 and air spring housing undergoes the same tilt, as does ring frame 198, bearings 194, bevel gears 20%) supported by the latter, and the oscillator drive gear driven from bevel gears 288 including the entirety of turret 224. This tilting action of these parts is permitted by sliding of arcuate bearing rings 174 and 176 on the arcuate part 171 of supporting plate 111, the relative sliding action of these arcuate parts taking place about center T as a pivot point. The reason for the channel shape of the support plate 111 will now be evident, in that this shaping accommodates the rocking action of the flange 181 above, and the air spring cover 143 below.

It will be seen that in this rocking or tilting action of the sleeve 18! flange 181, and ring frame 198 relative to the supporting plate 111, the blocks 301 carried by the ring frame simply pivot in the slots 30-2 in the brackets 3113 rising from the ring frame, thus accommodating for the relative pivotal action of the two groups of components involved. 7

' It will also be seen, particularly from FIG. 7, that the arcuate splines of the ends at shafts 96 permit the bevel gears 192 to tilt through the necessary angle without interfering with the drive from shafts 86 and the engines. Plate 111 can, under these conditions, swing about the trunnion axis afforded by the collars 181 pivoted on the hubs or trunnions 76, though this trunnion axis primarily serves another purpose, as will be mentioned hereinafter.

It has been mentioned that the pile may tend to turn on its axis during driving, and this is deemed to be an advantage. The present machine has been so contrived as to promote or increase the tendency for twisting, since twisting of the pile during driving has the beneficial effect of decreasing friction between the pile and the earth. The reaction of the ring gear 221 driving the turret mounted gear trains is such as to exert a torque on the turret frame 232, and this torque causes the turret frame to rotate slowly on bearing bushings 235 and 240.

' The turret frame is keyed to the oscillator body by means of two oscillator body wings 137a received in vertical slots 310 in brackets 311 (FIGS. 8 and 9) mounted on turret frame 232. Vertical bearing inserts 312 are preferably used in the bracket slots. The turret frame, rotating as described, thus acts through this keyed connection to rotate the oscillator body and with it the column 41 and the pile. The turret frame is thus rotatable relative to the ring frame 198 to cause slow rotation of the pile during driving, for example, but without limitation, six revolutions of the pile during complete driving of a pile.

The oscillator 42, turret 224, and associated parts, are covered by a bonnet 315 removably flange-connected at $16 to a ring 317 welded to the aforementioned ring 1112. Below the housing wall 104 are housing sections 318, 319 and 320 (FIGS. 6 and 8), which are bolted to one another through abutting flanges, and the lowermost section 3213 supports a plate 321 carrying an oil seal element 321:: which engages and seals to the bottom of air spring bottom wall 147. Lubricating oil is maintained in the bottom housing h'made up of these components, as to the level 0, in FIG. 6, and is circulated by means of a pump 322 (FIG. 6) mounted on housing section 319. The pump 322 is driven from a sprocket 323 on sleeve 79 through a chain 324 and sprocket 325 on the shaft of the pump. The oil is maintained in the housing by the seal at 321, the seal supporting plate 321 being resiliently flexible, and moving with any motion of the air spring housing 154 to preserve the seal.

The lubricating oil pump 322 receives oil from the sump inside housing h via a hose 481), and discharges oil under pressure into hose 45.1 (PIGS. 6, 11 and 12). Hose 401 leads to adjustable pressure relief valve 482 (FIGS. 11 and 12) which has return line 4113 to the housing h for oil discharged at excess pressure. The main discharge outlet from valve 482 is connected to filter 404 mounted on the side of housing section 319, and connects to hose 4G5 (FIGS. 11 and 12) leading to a fitting 486 mounted on the rim of air spring cover 143. Fitting 40-6 communicates with an oil passage 487 (FIG. 16) in cover 147 and extending up and through the tubular lower end portion 1'78 of sleeve 189 to discharge to the space adjacent bearing bushing 228, which it lubricates. This oil also rises through suitable oilgrooves, not shown, to lubricate bushings 213 and 215, and various oil passages are indicated in the drawings, but need not be explained in detail, by which lubricant from this source provides lubrication for various bearings of the mechanism.

A fitting 418 (FIG. 12) mounted inside housing member 319, alongside fitting 15612, has an external connector 411 fed by a hose leading from a suitable source, not shown, of a mixture of oil and air under pressure. The air carries the lubricant in finely divided particles as a mist, and distributes it to bearing surfaces reached by the air. To fitting 418 is connected hose 414 1eadingto fitting 415 on the rim of air spring cover (FIGS. 12 and 17). A passage 416 in air spring cover 143 connects fitting 415 with an annular channel 417 encircling air spring head 126, between piston rings 145, and connected via passage 418 to the lower end of a tube 419 set into head 126, and rising therefrom,through stem 132, into a bore 429 in the bottom of oscillator base 136. The upper end of tube 419 is packed in bore 420, and com municates with oil passages 422 leading outward through opposite sides of the base part 136 of oscillator body 137.

Mounted over the openings of the passages 422 are boxes 424 (FIG. 18) having hollow arms 425 extending toward the axes of the two crankshafts 284, and coupled at 426, in any suitable fashion, to hollow arms 427 extending from caps 428 mounted on the end plates 276 on the sides of the oscillator housing opposite from the drive shafts 265. The arms 427 have bores 430 communicating with the hollow arms 425, and caps 428 have internal tubular-projections 431 communicating with said bores 430 and with longitudinal bores 432 through crank shafts 284, the projections 431 being received and sealed within counterbores in the ends of the crankshafts as shown in FIG. 18.

The oil mist supplied to'the tube 419 is thus conveyed to the bores 432 in the crankshafts. Communicating with these bores 432 are cheek plate bores 448 which have branches 441 and 442 leading toward and supplying lubr cating oil mist to the various bearing surfaces in the crank mechanism and servo-roller system. The details of these arrangements need not be explained, as they may vary at will, and are within the ordinary skill of the mechanical designer. i 

18. A SONIC DRIVER FOR A PILE OR THE LIKE, COMPRISING: A SONIC OSCILLATOR EMBODYING A RELATIVELY MASSIVE BODY MEANS FOR COUPLING SAID OSCILLATOR BODY TO A PILE OR THE LIKE TO BE DRIVEN; SAID OSCILLATOR BODY HAVING THEREIN A CYLINDRICAL RACEWAY HAVING A CENTRAL LONGITUDINAL AXIS CONTAINED IN A PLANE PREPENICULAR TO THE AXIS OF THE PILE; AN INERTIA ROLLER OF LESS MASS THAN SAID BODY IN AND ADAPTED TO ROLL AROUND SAID RACEWAY IN AN ORBITAL PATH, SID ROLLER HAVING A CO-AXIAL RACEWAY THEREIN; A SMALLER ROLLER IN SAID RACEWAY IN SAID FIRST MENTIONED ROLLER ADAPTED TO ROLL THEREAROUND IN AN ORBITAL PATH AND TO THEREBY ROLL SAID FIRST MENTIONED ROLLER IN ITS ORBITAL PATH AROUND SAID FIRST MENTIONED RACEWAY; A ROTATABLE ARM MOUNTED AT ONE END ON SAID BODY FOR ROTATION ABOUT AN AXIS CO-AXIAL WITH SAID RACEWAY IN SAID BODY; A PIN PARALLEL TO THE AXIS OF ROTATION OF SAID ARM CARRIED BY THE FREE SWINGING END OF SAID ARM; AND AN ECCENTRIC BUSHING ON SAID PINE MOUNTING SAID SECOND MENTIONED ROLLER FOR ROTATION ON ITS AXIS. 